Stein



March 24, 1964 R. STEIN 3,125,905

RIVET SETTING MACHINE Filed Sept. 28, 1961 4 Sheets-Sheet 1 INVENTOR. RAPHAEL STEIN Maw ATTORNEY March 24, 1964 R. STEIN RIVET SETTING MACHINE 4 Sheets-Sheet 2 Filed Sept. 28, 1961 INVENTOR.

RAPHAEL STEIN M MW ATTORNEY March 24, 1964 R. STEIN 3,125,905

RIVET SETTING MACHINE INVENTOR. --26 RAPHAEL STEIN A TTORN EY March 24, 1964 R. STEIN 3,125,905

RIVET SETTING MACHINE Filed Sept. 28, 1961 I 4 Sheets-Sheet 4 9 202 f I L\\ I20 I62 x i I28 |g4 I I 206% k I a 1010) [30 7&7

1 I I I35 I22 INVENTOR.

RAPHAEL STEIN BY 68AM Kw- ATTORNEY United States Patent 3,125,905 RIVET SETTING MACHINE Raphael Stein, 1363 Meetinghouse Road, Huntingdon Valley, Pa. Filed Sept. 28, 1961, Ser. No. 141,398 13 Claims. (Cl. 7848) This invention relates to a rivet setting machine.

Many rivet setting machines have been proposed heretofore. In general, substantially all rivet setting machines are provided with off-set jaws. I have found that the off-set nature of such jaws, after substantial use, causes a rivet to be improperly set so that such rivet does not properly perform its intended function. This disadvantage in the rivet setting machines proposed heretofore has been overcome by the present invention wherein symmetrical jaws are provided.

In order to assure that the rivet is properly set and extending through aligned holes in sheet-like members, the rivet setting machine of the present invention delivers smooth spring pressure and then a hammer blow to the rivet before the main pressure is applied to the rivet to deform the same. The hammer blow is of a sufficient strength so as to partially deform the rivet thereby assuring that the sheet-like materials cannot move relative to each other when the main pressure is being applied to the rivet to deform the same. This feature of the present invention overcomes the disadvantage with the rivet setting machines proposed heretofore wherein a slight amount of relative movement between the sheet-like members causes the holes therein to be misaligned whereby the main pressure applied to the rivet deforms the same without joining the sheet-like materials.

In the rivet setting machines proposed heretofore, it has been conventional to transfer rivets from a raceway to a throat-block or the like by means of a reciprocating shuttle. Shuttles of this nature have not been entirely satisfactory since small amounts of oil, dirt, or burrs on the rivets prevents the lowermost rivet from entering the slot in the shuttle. As a result thereof, jamming of the shuttle and rivets has been common heretofore. The present invention overcomes this disadvantage by utilizing a positive transfer means. The positive transfer means of the present invention comprises an arcuate finger which rubs against the lowermost rivet in the raceway thereby rotating the same. Rotation of a lowermost rivet in the raceway assures the dropping of said rivet into the transfer slot, wherein such finger will physically push the rivet to the feed slot of the throat plate.

Heretofore, the rivet-setting machines have been generally provided with a mechanical power means which had limited the size of rivets which may be set with the particular machine. For example, a riveting machine is commercially available which can set rivets up to onequarter inch in diameter. If it is desired to utilize rivets of a greater diameter, a different machine must be utilized, with such additional machine only being capable of being used with larger size rivets than one-quarter inch in diameter. The rivet-setting machine of the present invention is more universal in that it may set rivets up to three-eighths of an inch in diameter.

Heretofore, when it was desired to change from oneeighth inch rivet to a one-quarter inch rivet, it was necessary to physically remove the raceway and the hopper associated therewith and replace the same with a larger size raceway and hopper. This disadvantage adds materially to the cost of the user of the machine since such user must purchase additional raceways and hoppers. Also, a substantial amount of down-time is associated with the substitution of a new hopper and raceway. Such down time is a costly inconvenience to the user of the rivet-setting machines proposed heretofore. The present 3,125,905 Patented Mar. 24, 1964 invention overcomes the disadvantages associated with substituting raceways and hoppers in a manner which is inexpensive and expeditious. In accordance with the present invention, only the rotor of the hopper and the raceway need be substituted when converting from one size rivet to another. As will be made clear hereinafter, the raceway of the present invention may be removed by merely removing two screws. Regardless of the size of the rivet capable of being set with the machine of the present invention, the hopper remains secured to the machine.

As pointed out above, it has been conventional heretofore to provide a mechanical motor having a heavy fly wheel to give momentum for applying pressure to the rivet to deform the same. The rivet-setting machine of the present invention is provided with a hydraulic motor means which is self-contained on the machine. The provision of a hydraulic motor means utilizing oil as a motive fluid enables the machine of the present invention to have several advantages over the prior art including the ability to convert from one size rivet to another by changing the power cylinder.

Rivet setting machines have been proposed heretofore wherein the motive fluid was compressed air. Such a machine requires the user to have an inner compressor, utilizes hoses of substantial length between the air cylinder and the compressor, requires air filters which must be checked and cleaned daily, etc. Such a machine requires substantially more floor space than the machine of the present invention, is substantially more expensive than the machine of the present invention, and is approximately one-third higher than the machine of the present invention.

It is an object of the present invention to provide a rivet-setting machine which is more universal than those proposed heretofore.

It is another object of the present invention to provide a rivet-setting machine wherein a hammer blow is delivered to the rivet prior to the application of the main force to the rivet.

It is still another object of the present invention to provide a rivet-setting machine having symmetrical jaws with respect to the rivet driver.

It is a still further object of the present invention to provide a rivet-setting machine which does not require the hopper to be removed when converting from one size rivet to another.

It is still another object of the present invention to providea novel transfer mechanism for feeding rivets from the raceway to the throat plate.

It is still another object of the present invention to provide a rivet-setting machine having a positive transfer feed mechanism for the rivets.

It is a further object of the present invention to provide a novel rivet-setting machine having a hydraulic power plant.

It is another object to provide a rivet setting machine which can have varied pressure by merely changing the power cylinder of the power plant.

It is a still further object of the present invention to provide a rivet-setting machine which is shorter, thinner, lighter in weight, simpler, and cheaper than rivet-setting machines proposed heretofore.

Other objects will appear hereinafter.

For the purpose of illustrating the invention there is shown in the drawings a form which is presently preferred; it being understood, however, that this invention is not limited to the precise arrangements and instrumentalities shown.

FIGURE 1 is a partial elevational view of the rivetsetting machine of the present invention with portions broken away for clarity of illustration.

FIGURE 2 is a sectional view taken along lines 2-2 in FIGURE 1.

FIGURE 3 is a sectional view taken along lines 3-3 in FIGURE 1.

FIGURE 4 is a view similar to FIGURE 3 showing the elements in another disposition.

FIGURE 5 is a view similar to FIGURE 3 showing the elements in still another disposition.

FIGURE 6 is a sectional View taken along lines 66 in FIGURE 1.

FIGURE 7 is an enlarged detail view taken along lines 77 in FIGURE 1.

FIGURE 8 is a top plan view of the driving linkage for the spindle.

FIGURE 9 is an enlarged detail view of the jaw and elements associated therewith in FIGURE 1.

FIGURE 10 is an enlarged detail view of the rivet feed slot.

FIGURE 11 is a schematic illustration of the hydraulic circuit of the power plant.

Referring to the drawings in detail, wherein like numerals indicate like elements, there is shown in FIGURE 1 a rivet-setting machine designated generally as it The rivet-setting machine 10 includes a frame 12 cast from metal. The frame 12 may be mounted on a table, or as illustrated on a pedestal support 14. An anvil arm 16 having an anvil 18 extends from the pedestal support 14 in the same direction and below the horizontally ex tending arm of the frame 12.

The horizontally extending arm of the frame 12 terminates in a guide portion 22 having an upright bore therethrough. A cylindrical driver guide sleeve 22 is reciprocably guided secured within such bore in the portion 20 by pin 21 on sleeve 22 and slot 19 in portion 20. A

cylindrical driver mechanism 24 is reciprocally disposed within and guided by a longitudinally extending bore in the driver guide sleeve 22. Spring 25 biases sleeve 22 against limit stop 23. A reciprocally disposed driver 26 extends from the lowermost end of the driver mechanism 24. The lowermost end of the driver 26 extends between spaced symmetrically disposed jaws 28 and 39. Each of the jaws 23 and 30 are mating halves of a rivet confining means.

The jaw 28 is supported from the guide sleeve 22 by a flat flexible jaw spring 32. The jaw 39 is supported from the guide sleeve 22 by a flat flexible jaw spring 34. The jaws 28 and 30 and the guide sleeve 22 are secured to the jaw springs 32 and 34 in any convenient manner such as by screws. As may be ascertained from a comparison of FIGURES 1, 2 and 9, the jaw springs 32 and 34, the driver mechanism 24, the driver 26, and the jaws 28 and 30 are symmetrically disposed.

As shown more clearly in FIGURES 3-5, the driver mechanism 24 comprises a sleeve member 36 having a solid portion 37 terminating in a pair of ears 38. The sleeve member 36 is concentric with and removably secured to a sleeve 40 by means of threads. The outer diameter of the sleeve 36 is identical with the outer diameter of the sleeve 40 and one end of the sleeve 36 is in abutting contact with a shoulder and on the sleeve 40. The sleeve 40 is threadably secured to a tip 42.

The driver 26 is reciprocally disposed within the tip 42. An annular flange 44 on the driver 26 abuts a shoulder 46 on :the tip 42 in the lowermost position of the driver 26. The annular flange 44 is biased into abutting contact with the shoulder 46 by means of a coil spring 48 extending between the flange 44 and an annular bushing 50. Bushing 50 is threadably secured to an inner peripheral surface on the tip 42.

The upper end of the driver 26 extends through the bushing 50 and a bore 54 in a cylindrical member 52. The cylindrical member 52 is guided for reciprocatory motion by the inner peripheral surface of the sleeve 41 In its lowermost position, the member 52 abuts the upper surface of the bushing 52. A cylindrical slider 55 is slidably disposed in a transverse bore in the member 52. The slider 55 is provided with a bore 56 which is slightly larger in diameter than the bore 54. As seen more clearly in FIGURE 3, the bore 56 is offset with respect to the bore 54 so that a shoulder formed by the reduced diameter portion 60 on the driver 26 may abut the lowermost surface 58 on the slider 55.

A tapered cam surface 62 is provided on the slider 55. As will be made clear hereinafter, the cam surface 62 is adapted to cooperate with the cam surface 64 to cause the slider 55 to move transversely within the bore in member 52 thereby aligning the bores 56 and 54.

An elongated back-up cylinder 66 integral with member 52 is disposed within the sleeve 40. The back-up cylinder 66 is provided with a blind hole 68 in line with bore The back-up cylinder 66 and member 52 are recessed so that a leafspring 70 may be removably secured thereto. The leafspring 70 biases the slider 55 to the left in FIGURE 3 thereby displacing the bore 56 with respect to the bore 54. The back-up cylinder 66 and member 52 are biased into abutting contact with the uppermost surface on the bushing 50 by means of a coil spring 72. The uppermost end on the spring 72 is in abutting contact with the solid portion 37.

One end of a link 74 is rotatably secured between the ears 38 on the sleeve member 36 of the driver mechanism 24. The other end of the link 74 is rotatably connected between a pair of ears on an arm 76. The arm 76 forms one leg of an L-shaped link 7 8. The link 78 is rotatably secured betwen a pair of ears 80 by means of a pin 82.

The arm 84 terminates in a pair of spaced ears and consists of the other leg of the L-shaped link 78. The arm 84 is rotatably secured to end 86 of piston rod 88. The end of piston rod 558 remote from end 86 extends into a power cylinder 90 and terminates at a piston 92. The power cylinder 9% has one end rotatably supported by a bracket 94 having spaced ears through which extends a pivot pin 96.

Flexible conduits 98 and 18% extend from opposite ends of the power cycle 99. The conduits 98 and 1% extend from a valve 132. The valve 162 is provided with a solenoid operator 1&4. Oil or a comparable hydraulic liquid is pumped from the reservoir 1% by means of pump 103 through the valve 102 and the conduits 98 and 100. The pump 1% is operated by means of the motor A main control switch 112 is provided on the support 14 for controlling the supply of electricity to the machine 10 of the present invention. After the main switch 112 has been turned on, the solenoid operator 104 land the motor 116 are responsive to a foot pedal operated switch 114.

As shown more closely in FIGURE 8, the piston rod 83 is provided with an O-shaped portion 116 intermediate its ends. The O-sha-ped portion 116 includes a pair of spaced parallel arms 118 and .120. A raceway or rivet guide rail 122 extends through the O-shaped portion 116 between the arms 11% and 122. The raceway 122 is provided with a slot 124 through which the shank portion of a rivet may extend.

As shown more clearly in FIGURE 7, the raceway 122 terminates in a throat plate 126 having a slot 128 forming a continuation above the slot 124. The slot 128 terminates at an arcuate transversely extending slot 130. One end of the slot 130 extends through a side wall of the plate 126. The other end of the slot 130 terminates in a slot 132 which is parallel to the slots 124 and 128. Rivets are fed between the jaws 28 and 34) from the slot 132.

An arcuate finger 134 may extend into the slot 130 until limit stop 135 contacts plate 126. The finger 134 is integrally connected to one end of a ii-shaped arm 136. The arm 136 is rotatably supported for rotation about a pivot pin 138 positioned at the apex of the arm 136. Rotation of the arm 136, and hence reciprocation of the finger 134 within the slot 130 is caused by an actuator rod 140. The rod 140 extends through a boss 142 on the horizontally disposed arm of the frame 12 and terminates in a cam follower 144. A spring 146 surrounds the rod 140 and extends between the cam follower 144 and the boss 142. The cam follower 144 cooperates with a cam surface 148 on the lowermost surface of the arm 120.

A coil spring 150 surrounds the rod 146'. The spring 150 extends between adjustable collar 152 and washer 154. The washer 154 is in abutting contact with a cylindrical rotatably mounted bushing on the arm 136. The lowermost end of the rod 140 extends through a bore in said bushing. Accordingly, as the rod 140 moves to the left in FIGURE 7 as a result of movement of the cam surface 148 to the left in FIGURE 1, a portion of the lefthand end of the rod 141} in FIGURE 7 overtravels the bushing on the arm 136 thereby compressing the spring 150. The energy of the compressed spring 150 rotates the arm 136 in a counterclockwise direction in FIGURE 7. Such counterclockwise movement of the arm 136 causes reciprocation of the finger 134 so that it may move to a position for pushing the next rivet in slot 124 to the slot 132.

As shown more clearly in FIGURE 1, a novel hopper 156 is provided for the machine 10. The hopper 156 is mounted on a bracket 158 so as to be positioned above the arms 118 and 120. The hopper 156 comprises a hollow cylinder 166 mounted on a planar base 162.

A rotor 164 is rotatably mounted within the cylinder 160 on the base 162 and shaft 166 supported by the base 162. The rotor 164 is maintained in contact with the juxtaposed surface of the base 162 by means of the wing nut 168.

The outer peripheral surface of the rotor 164 is spaced from the inner peripheral surface of the cylinder 160 by a distance slightly larger than the thickness of the head portion of the rivet currently being used on the machine 10. A plurality of radially extending recesses 170 are provided on the outer periphery of the rotor 164. The width and length of the recesses 170 are slightly larger than the corresponding dimensions of the shank portion of the rivet currently being used on the machine 10. A slot 172 is provided in the base 162 in line with one of the recesses 170. The width of the slot 172 corresponds with the width of the recesses 170. Accordingly, a rivet having its shank portion in one of the recesses 170 may fml through the slot 172 into the raceway 122 with the shank portion of the rivet extending through the slot 124 on the raceway 122.

A bore is provided in the base 162 diametrically opposite the position of the slot 172. A detent 176 is spring biased within said bore in a direction toward the rotor 164. As the rotor passes over the detent 176, the detent 176 is biased against its spring in a direction away from the rotor 164. Contact between the rotor 164 and the detent 176 provides for a slight hesitancy in the rotation of the rotor 164 so as to enable the rivet to fall through the slot 172. A coil spring 174 is supported the cylinder 160 and extends to a point adjacent the rotor 164 so as to spin rivets disposed the cylinder 160. In practice, the cylinder 160 will be made from a piece of seamless tubing and provided with a cover not shown.

An actuator plate 178 and a ratchet 180 are supported on the shaft 166 below base 162. The ratchet 180 is keyed to the shaft 166. A pawl 182 is rotatably supported on the plate 178 for rotation about pin 184. A hair spring 186 biases the pawl 182 into engagement with the ratchet 180. A coil spring 188 biases the plate 178 toward limit stop 189. Limit stop 189 may be a rod depending from base 162.

The bias of spring 188 is opposed by the force imported to the plate 178 by shaft 190. The shaft 190 is connected to plate 176 by a ball and socket connection 192.

A shaft 194 has one end removably connected to the free end of shaft 190. The other end of shaft 194 is connected to an actuator arm 19 8 by a ball and socket connection 196. The arm 198 is supported by arm 120. The shank portion of bolt 202 extends through a longitudinally extending slot 204 on arm 198 and is threadably secured to stud 201).

The operation of the rivet setting machine 10 is as follows:

It will be assumed that the elements are in the position illustrated in FIGURES 1, 2, 6, 7 and 9. The hopper 156 will have an adequate supply of rivets and a plurality of such rivets will be disposed so that their shank porti-ons extend through the slot 124 of the raceway 122 as illustrated in FIGURE 1. The main switch 112 will be on and a rivet will be disposed between the jaws 28 and 30 as shown more clearly in FIGURES 2 and 9 with another rivet disposed within the throat plate as illustrated in FIGURE 9.

When it is desired to rivet the sheet like materials together, the operator steps on the foot actuator switch 114. Actuation of the switch 114 couples electricity to the solenoid 1114 which shifts a spool within the valve 102 to a disposition so that a hydraulic liquid such as oil is pumped from the reservoir 186 through intake filter 10 7, pump 108, through valve 162 and conduit to cylinder 90. The oil pressure may be observed on gage 111. As oil is pumped through conduit 100 into the cylinder 96, piston 92 and the piston rod 88 move to the left in FIGURES 1 and 8. As will be made clear hereinafter, movement of the piston rod 8 8 to the left in FIGURES 1 and 8 enables the rotor 164 to be rotated, the rod to be reciprocated toward the jaws 28 and 30; and the driver 24 to be reciprocated toward the anvil 18.

As the piston rod 88 moves to the left in FIGURE 1, it will be seen that the L-shaped link 78 rotates about the pin 82 thereby moving the driver mechanism 24 down- Wardly in FIGURE 1. The driver mechanism 24 reciprocates downwardly with the driver 26 contacting the rivet 266 between the jaws 2S and 30. Downward movement of the driver 26 causes the head of the rivet 206 to move the jaws downwardly against the bias of spring 25 and spreads the jaws 28 and 3t) apart thereby enabling the shank portion of the rivet 206 to enter the aligned holes in the sheet-like material. When the end of the shank portion of the rivet contacts the anvil 18, the various elements of the driver mechanism 24 are in the position illustrated in FIGURE 3. Thereafter, the contact between the rivet and the anvil 18 causes the driver 26 to reciprocate upwardly in FIGURES 1 and 3. As the driver 26 reciprocates vertically, the spring 48 is compressed and the shoulder at the upper end of the driver 26 contacts the lower surface 58 of the slider 55. The driver 26 continues to move upwardly until the cam 62 contacts the cam surface 64 thereby moving the slider 55 to the right in FIGURE 4 against the pressure of the leaf spring 79.

As soon as the bore 56 in the slider 55 is in line with the driver 26 so that the spindle may enter the same, the previously compressed spring 72 expands thereby moving the back up cylinder 66 downwardly until the end wall 69 in the hole 68 contacts the uppermost end of the extension 60 on the driver 26. Contact between the end Wall 69 and the uppermost end of the extension 60 delivers a hammer blow of approximately forty to fifty pounds to the driver 26. This hammer blow is delivered by the driver 26 to the rivet which is extending through the aligned holes in the sheet-like materials as described above. This hammer blow enables the anvil 18 to slightly deform the adjacent end of the shank portion of the rivet 2116. At this point, relative motion between the sheet-like materials is precluded and assurance that the shank portion of the rivet is extending through the aligned holes of the sheet-like materials prior to delivery of the main force is obtained.

The spring 48 within the driver mechanism 24 merely provides a very light bias on the driver 26 so as to prevent random movement of the driver 26, rattling thereof, etc. After the hammer blow has been delivered to the rivet, the driver 26 continues to reciprocate upwardly in FIGURE until the flange 44 contacts the lowermost end of the bushing 50. Thereafter, the main force for deforming the rivet is transmitted to the rivet through such engagement between the flange 44 and the bushing 50. The reciprocatory movement of the driver mechanism 24 is guided by the driver guide sleeve 22 so that the driver mechanism 24 reciprocates in a vertical direction. To accommodate the are through which the end 86 of the piston rod 88 will travel, the righthand end of the cylinder 90 in FIGURE 1 is rotatably mounted about the pin 16.

As the rivet 266 is forced out of its disposition between the jaws 28 and 31 by the spindle 26, the jaws 23 and 3% separate. Such separation of the jaws 28 and 3t? and the springs 32 and 34 are symmetrical about the driver 24, uniform separation in opposite directions results so that positive assurance against cocking of the rivet is attained.

As the piston rod 88 moves to the left in FIGURES 1 and 8, the cam surface 148 cooperates with the cam follower 144 to reciprocate the rod 140 in a direction toward the jaws 28 and 30. Such movement of the rod 1411 results in a compression of the spring 146. As the rod 1415 moves to the left in FIGURE 7, the rod 140 passes through the bushing supported by the arm 136 thereby compressing the spring 15% between the adjustable collar 152 and the washer 154. Compression of the spring 150 results in a smooth application of pressure to the arm 136 thereby rotating the same in a counterclockwise direction in FIGURE 7. Such rotation of the arm 136 causes the finger 134 to reciprocate in the slot 1% until the end of the finger 134 is below the slot 124. As the finger 134 reciprocates in the slot 131 a side edge thereof engages the shank portion of the lowermost rivet thereby rotating the same. Such rotation of the lowermost rivet assures that it is free to fall into the slot 131) as soon as the end of the finger 134 clears the slot 124.

As the piston rod 83 moves to the left in FIGURES 1 and 8, the stud 2% and the bolt 202 on the arm 120 likewise move to the left. Such movement of the arm 120 enables the spring 188 to rotate the plate 1'78 in a counterclockwise direction in FIGURE 6 until the plate 178 abuts the limit step 189. This rotation of the plate 178 repositions the pawl 182 with respect to the ratchet 180. As the arm 1211 continues to move to the left, the shank portion of the bolt 2'62 reciprocates along the lengt of the slot 204. The ball and socket joints 192 and 196 facilitate the pivoting movement of the arm 198 as a result of the reciprocation of the arm 120.

It will be appreciated that all of the above steps in the operation of the machine it), subsequent to actuation of the pedal operated switch 114, takes place within a very short period of time which may be from /2 to two seconds. After the rivet 2&6 has been set and deformed so as to fixedly secure the sheet-like materials together, the spool Within the valve 102 will resume its normal disposition wherein the oil is being pumped from the reservoir 106 through the conduit 98 into the cylinder 91!. In such disposition, the conduit 1% is in communication with the reservoir 1% through the valve 102. As the piston rod 88 resumes the position shown in FIGURES 1 and 8, the rotor 164 is rotated through a predetermined arc, the driver 24 reciprocates to the position shown in FIGURE 1, and the rod 140 is biased upwardly to the position shown in FIGURE 1 as will be made clear hereinafter.

After a predetermined amount of travel of the arm 12!) in the return direction, the shank portion of the bolt 202 contacts the end of the slot 2% thereby rotating the plate 178 from a position abutting the limit stop 189 to the solid line position shown in FIGURE 6. Such rotary movement causes the pawl 132 to rotate the ratchet 1841. Since the ratchet 180 is keyed to the shaft 166, the rotor 164 rotates through a predetermined are so as to place another recess 17@ over the slot 172. As a result of the rotary movement of the plate 178, the spring 188 is expanded so that it may maintain Contact between the bolt 202 and the arm 128 on the next stroke.

As the arm 12% reeiprocates to the right in FIGURES 1 and 8, the spring 146 expands thereby keeping the cam follower 144 in contact with the cam surface 148 and reciprocating the rod 1451 in a direction away from the jaws 28 and 313. At the same time, the spring 150 expands thereby enabling the arm 136 to rotate in a clockwise direction in FIGURE 7 so that the end of the finger 134 may push the rivet resting thereon to a position so that it may have its shank portion disposed within the slot 132. Thereafter, such rivet 2% slides due to gravity along the slot 132 to the disposition illustrated in FIGURE 9.

As the piston rod 88 reciprocates to the right in FIG- URES 1 and 8, the link 78 rotates in a clockwise direction in FIGURE 1 thereby causing the driver mechanism 24 to reciprocate vertically within its guide sleeve 22. As the driver mechanism 24 reciprocates vertically, the spring 43 expands until the flange 44 abuts the shoulder 46. Thereafter, the driver 26 is raised vertically until its lowermost end clears the end of the throat plate 126. Thereafter, the next rivet 206 may fall to a disposition between the jaws 28 and 3t).

Thereafter, the above cycle may be repeated by the operator stepping on the pedal operated switch 114. The operator need only step on the switch 114 momentarily so as to couple the solenoid 164 with a source of current. The temporary coupling of current to the solenoid 104 is suflicient to reciprocate the spool within the valve 102 to one of its operative positions, for a sufiicient period of time so that oil may be pumped into cylinder 91) through conduit 100. Thereafter, such spool will move to its opposite position under the influence of a spring or the like. The main pressure will be applied to the rivet so long as the operator maintains pressure on the switch 114. Excess pressure will be relieved by relief valve 109 which recirculates the liquid back to the reservoir 106.

When it is desired to convert from one size rivet to another, bolt 208 and another bolt, not shown, are removed. This enables the raceway 122 to be free from securement with respect to the machine 10 so that a different size raceway may be substituted therefor. The rotor 164 may be removed by adjustment of the wing nut 168. Thereafter, a new rotor may be substituted. Thus, it will be seen that the machine 10 may be converted from one size rivet to another in a very expeditious manner result ing in very little down time.

The rails of the raceway 122 must be kept smooth and clean as well as free from oil and dust. This facilitates free feeding of the rivets. When the main pressure is being applied to the rivet, the jaws 28 and 30 should be spaced from the sheet-like materials and the head of the rivet extending through such materials by a distance of approximately of an inch. Such spacing is attained by adjustable limit stop 212 which is threaded to car 214 on sleeve 22. The limit stop 212 extends into a slot 216 in portion 20 and is in the up position in FIGURE 2. Slot 216 is wider than ear 214. The diameter of the spindle 26 is slightly smaller than the diameter of the head of the rivet and is provided with a concave or other shaped surface on its lowermost end so as to accommodate and mate with the shape of the head of the rivet.

Thus, it will be seen that I have provided a novel rivet setting machine having symmetrical jaws, means for delivering a smooth spring pressure and a hammer blow to the rivet prior to the application of the main pressure, a novel hopper, a novel transfer mechanism for the rivets, and a novel power plant. These features provide for more positive assurance of trouble-free operation, pro- 'vide a machine which is lighter in weight, smaller in size, easier to convert from one type of rivet to another, and capable of being utilized with a greater range of rivets. It will be appreciated that the hammer blow force may be adjusted by adjusting the tension on the spring 72 and that the main force for deforming the rivet may be adjusted by regulating the pump speed and opening in the valve 192.

The present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof and, accordingly, reference should be made to the appended claims, rather than to the foregoing specification as indicating the scope of the invention.

I claim:

1. A rivet setting machine comprising a frame supporting a reciprocably mounted driver mechanism, a stationary anvil in line with said mechanism, a pair of jaws, spring members on diametrically opposite sides of said mechanism, said members supporting said jaws for movement toward and away from one end of said driver mechanism, a hopper, a rotor rotatably mounted within said hopper, said rotor having peripheral recesses, and a hydraulic means for selectively reciprocating said driver mechanism toward and away from said anvil, said hydraulic means including a closed circuit having a liquid reservoir of motive liquid adapted to be pumped into pposite sides of a piston in a power cylinder, and linkage means connecting said piston to said rotor and said driver mechanism.

2. A rivet setting machine comprising a frame supporting a reciprocably mounted driver mechanism, an anvil in line with said mechanism, means for selectively reciprocating said mechanism toward and away from said anvil, a pair of jaws, spring means supporting said jaws for movement toward and away from said mechanism, a raceway for delivering rivets to a throat plate adjacent said jaws, a slot in said raceway for accommodating the shank portion of a rivet, a slot in said throat plate for accommodating the shank of a rivet, said slots being offset with respect to one another, an arcuate transfer slot interconnecting said slots, and a transfer mechanism for selectively pushing only one rivet at a time from said raceway slot through said transfer slot to said throat plate slot said transfer mechanism including an arcuate finger on a rotatably mounted arm, said finger extending into said transfer slot for abutting rotative engagement with the lowermost rivet in the raceway slot.

3. A machine in accordance with claim 2 wherein said spring means include a flat resilient leafspring for each jaw, and said leafsprings and jaws and driver mechanism being symmetrical with respect to one another.

4. A rivet setting machine in accordance with claim 2 including an actuating rod for said rotatably mounted arm,

said rod being coupled to said arm through a compressible member when said rod moves in one direction, and said rod being coupled to said arm by direct contact when moving in an opposite direction.

5. A rivet setting machine comprising a frame supporting a reciprocably mounted driver mechanism, a pair of jaws, spring means on diametrically opposite sides of said mechanism supporting said jaws for movement toward and away from each other, said driver mechanism including a cylindrical housing, a reciprocably mounted spindle disposed within said housing and having one end extending from said housing to a point between said jaws, means coupled to one end of said housing for selectively reciprocating said housing toward and away from said jaws and applying pressure through said spindle to deform a rivet, and means in said housing for selectively delivering a hammer blow to said spindle, said means for selectively reciprocating said housing including a rod, means for intermittently receiving rivets from a hopper to a raceway in response to movement of said rod, and means r 10 for transferring rivets from said raceway to a throat plate in response to movement of said rod.

6. A machine in accordance with claim 5 including a power cylinder surrounding a piston on one end of said rod, means providing a closed hydraulic circuit between said cylinder and an oil reservoir, and means for selectively pumping oil from said reservoir into said cylinder in response to a pedal operated switch.

7. A machine in accordance with claim 5 including a cylindrical reciprocally mounted sleeve surrounding said housing, said spring means being connected to said cylindrical sleeve.

8. A rivet setting machine comprising a frame supporting a reciprocably mounted driver mechanism, linkage interconnecting said mechanism with a rod so that said mechanism reciprocates in response to reciprocatory motion of said rod, a pair of jaws, a pair of springs on diametically opposite sides of said mechanism supporting said jaws for movement toward and away from each other, said mechanism including a spindle adapted to have a position between said jaws, means for selectively and intermittently feeding rivets between said jaws, said last mentioned means including a rod reciprocally guided by said frame and having a cam follower biased into contact with a cam on said first mentioned rod.

9. A rivet setting machine comprising a frame supporting a reciprocably mounted driver mechanism, a stationary anvil in line with said mechanism, a pair of jaws, flat springs supporting said jaws for movement toward and away from a spindle extending from said mechanism, said springs and jaws being symmetrical with respect to said spindle, a piston rod having its longitudinal axis substantially perpendicular to the longitudinal axis of said mechanism, linkage means interconnecting one end of said rod with one end of said mechanism for transferring the motive power of said rod to said mechanism so that said mechanism may cooperate with said stationary anvil to deform a rivet therebetween, means for intermittently feeding rivets from a hopper to a raceway in response to the movement of said rod, means for intermittently transferring rivets from said raceway to a throat plate in response to movement of said rod, and a hydraulic means for selectively reciprocating said rod, said hydraulic means including an oil reservoir supported by said frame and means for pumping oil from said reservoir to opposite sides of a piston on said rod disposed within a power cylinder.

10. A machine in accordance with claim 9 including means in said mechanism for delivering a hammer blow to said spindle.

11. A machine in accordance with claim 9 wherein said means for transferring rivets from said raceway to said throat plate includes a rotatably mounted arm, a finger on said arm, an end of said finger extending through a slot which interconnects a slot in said raceway and a slot in said throat plate, said slots in said throat plate and raceway extending in substantially parallel planes offset from one another, a spring abutting said arm, said finger extending to said throat plate slot in the fully extended position of said spring, and a rod for compressing said spring in response to movement of said piston rod whereby said end of said finger moves to a position wherein the lowermost rivet in said raceway slot may move into said interconnecting slot.

12. A rivet setting machine comprising a frame supporting a reciprocally mounted driver mechanism, an anvil in line with said mechanism, a pair of jaws, flat springs on diametrically opposite sides of said mechanism, said springs supporting said jaws for movement toward and away from a spindle extending from said mechanism, a piston rod having its longitudinal axis substantially perpendicular to the longitudinal axis of said mechanism, linkage means interconnecting one end of said rod with one end of said mechanism, a hopper above said piston rod, a rotatable rotor in said hopper, means coupling said piston rod to said rotor so that said rotor is rotated in response to movement of said piston rod, a raceway means extending from said hopper to said jaws and having ofiset slots, means for pushing rivets one at a time from one raceway slot to another in response to movement of said piston rod, a closed circuit hydraulic means for selectively reciprocating said piston rod, said hydraulic means including an oil reservoir supported by said frame and a cylinder, a piston on said piston rod, said piston being in said cylinder, and a pump coupled to said reservoir and cylinder for selectively pumping oil from said reservoir to opposite sides of said piston.

13. A machine in accordance with claim 12 wherein said mechanism includes means for delivering a hammer so. low to a rivet prior to cooperation of said spindle and anvil for deforming a rivet.

References Cited in the file of this patent UNITED STATES PATENTS 1,191,180 Havener July 18, 1916 1,651,976 Stirnpson Dec. 6, 1927 2,101,924 Turnquist Dec. 14, 1937 2,306,851 Ward Dec. 29, 1942 2,774,133 Sitz Dec. 18, 1956 3,030,833 Siegel et al. Apr. 24, 1962 FOREIGN PATENTS 29,222 Great Britain 1913 

1. A RIVET SETTING MACHINE COMPRISING A FRAME SUPPORTING A RECIPROCABLY MOUNTED DRIVER MECHANISM, A STATIONARY ANVIL IN LINE WITH SAID MECHANISM, A PAIR OF JAWS, SPRING MEMBERS ON DIAMETRICALLY OPPOSITE SIDES OF SAID MECHANISM, SAID MEMBERS SUPPORTING SAID JAWS FOR MOVEMENT TOWARD AND AWAY FROM ONE END OF SAID DRIVER MECHANISM, A HOPPER, A ROTOR ROTATABLY MOUNTED WITHIN SAID HOPPER, SAID ROTOR HAVING PERIPHERAL RECESSES, AND A HYDRAULIC MEANS FOR SELECTIVELY RECIPROCATING SAID DRIVER MECHANISM TOWARD AND AWAY FROM SAID ANVIL, SAID HYDRAULIC MEANS INCLUDING A CLOSED CIRCUIT HAVING A LIQUID RESERVOIR OF MOTIVE LIQUID ADAPTED TO BE PUMPED INTO OPPOSITE SIDES OF A PISTON IN A POWER CYLINDER, AND LINKAGE MEANS CONNECTING SAID PISTON TO SAID ROTOR AND SAID DRIVER MECHANISM. 